US5477820A - Thermal management system for heat engine components - Google Patents

Thermal management system for heat engine components Download PDF

Info

Publication number
US5477820A
US5477820A US08/315,162 US31516294A US5477820A US 5477820 A US5477820 A US 5477820A US 31516294 A US31516294 A US 31516294A US 5477820 A US5477820 A US 5477820A
Authority
US
United States
Prior art keywords
piston
engine
coating
heat
combustion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US08/315,162
Other languages
English (en)
Inventor
V. Durga N. Rao
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KSU INSTITUTE FOR COMMERCIALIZATION
Ford Global Technologies LLC
Kansas State University Institute for Commercialization
Original Assignee
Ford Motor Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ford Motor Co filed Critical Ford Motor Co
Priority to US08/315,162 priority Critical patent/US5477820A/en
Assigned to FORD MOTOR COMPANY reassignment FORD MOTOR COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RAO, V. DURGA NAGESWAR
Priority to DE19524015A priority patent/DE19524015C2/de
Priority to JP7192066A priority patent/JPH08100659A/ja
Priority to GB9516811A priority patent/GB2293863B/en
Priority to CA002159232A priority patent/CA2159232A1/en
Application granted granted Critical
Publication of US5477820A publication Critical patent/US5477820A/en
Assigned to MID-AMERICA COMMERCIALIZATION CORPORATION, A CORP. OF KANSAS reassignment MID-AMERICA COMMERCIALIZATION CORPORATION, A CORP. OF KANSAS ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FORD MOTOR COMPANY
Assigned to FORD GLOBAL TECHNOLOGIES, INC. A MICHIGAN CORPORATION reassignment FORD GLOBAL TECHNOLOGIES, INC. A MICHIGAN CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FORD MOTOR COMPANY, A DELAWARE CORPORATION
Assigned to MID-AMERICA COMMERCIALIZATION reassignment MID-AMERICA COMMERCIALIZATION CORRECTIVE ASSIGNMENT TO CORRECT THE ASSIGNOR, PREVIOUSLY RECORDED AT REEL 011369 FRAME 0412. Assignors: FORD GLOBAL TECHNOLOGIES, INC.
Assigned to FORD GLOBAL TECHNOLOGIES, LLC reassignment FORD GLOBAL TECHNOLOGIES, LLC ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NATIONAL INSTITUTE FOR STRATEGIC TECHNOLOGY ACQUISITION AND COMMERCIALIZATION
Assigned to NATIONAL INSTITUTE FOR STRATEGIC TECHNOLOGY ACQUISITION AND COMMERCIALIZATION reassignment NATIONAL INSTITUTE FOR STRATEGIC TECHNOLOGY ACQUISITION AND COMMERCIALIZATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: MID-AMERICA COMMERCIALIZATION CORPORATION
Assigned to KSU INSTITUTE FOR COMMERCIALIZATION reassignment KSU INSTITUTE FOR COMMERCIALIZATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: MID-AMERICA COMMERCIALIZATION CORPORATION, NATIONAL INSTITUTE FOR STRATEGIC TECHNOLOGY ACQUISITION AND COMMERCIALIZATION
Assigned to KANSAS STATE UNIVERSITY INSTITUTE FOR COMMERCIALIZATION reassignment KANSAS STATE UNIVERSITY INSTITUTE FOR COMMERCIALIZATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: KSU INSTITUTE FOR COMMERCIALIZATION
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B77/00—Component parts, details or accessories, not otherwise provided for
    • F02B77/11—Thermal or acoustic insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/18—DOHC [Double overhead camshaft]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F2001/244—Arrangement of valve stems in cylinder heads
    • F02F2001/245—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/02—Light metals
    • F05C2201/021—Aluminium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
    • F05C2201/0448—Steel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/16—Fibres

Definitions

  • This invention relates to the art of designing and fabricating pistons and related heat engine component surfaces for a fossil fueled engine, which surfaces affect the conversion of chemical energy to mechanical energy and which affect emissions resulting from the combustion process; more particular the invention relates to combustion chamber and charge induction surfaces, including piston designs and materials that (i) can store and release heat selectively, (ii) control or limit temperature of piston and component surfaces, or (iii) control or inhibit thermal expansion of components, primarily pistons, in an internal combustion engine (IC).
  • IC internal combustion engine
  • thermal barriers Teflon in U.S. Pat. No. 2,817,562; nickel metal in U.S. Pat. No. 5,158,052; and chromium oxide in U.S. Pat. No. 4,735,128,.
  • thermal barriers are insufficient to manage heat properly because they must be unduly thick thereby adversely affecting volumetric efficiency (i.e. allowing too much stored heat to be transferred to the induction charge); no provision is made to remove the stored heat from the combustion chamber surfaces independent of charge absorption.
  • Such heat management leads to greater volumetric efficiency of the engine, a reduction in emissions, and an increase in engine power while permitting an increase in compression ratio for a gasoline engine.
  • the invention is a heat engine piston and combustion chamber construction that employs a low thermal diffusivity coating which functions as a heat transfer diode, that is, the coating restricts heat flow from the combustion chamber during combustion while allowing some limited heat transfer during the expansion and exhaust strokes of the piston; the coating limits or prevents the stored heat from flowing into the fresh combustible charge during the intake and compression strokes.
  • diffusivity is inversely proportional to density and mass specific heat capacity of the coating material, the material must be selected with attention to more than thermal conductivity, the latter being solely characteristic of prior art selections.
  • the thickness of the low diffusivity diode coating is important because it muse be minimal while having sufficient mass to assure appropriate thermal transfer behavior.
  • the invention is a method of thermally managing heat generated by an internal combustion engine no increase power and fuel economy.
  • the method comprises: (a) increasing the compression ratio of the engine by 10-20%; (b) coating the crown of the piston and combustion chamber surfaces with a low thermal diffusivity layer Than functions as a heat diode; and (c) operating the engine with such coating crown and surfaces using the increased compression ratio whereby a fresh intake mixture to the combustion chamber will be drawn thereinto at a much lower temperature for a higher volumetric efficiency with less heat from the combustion chamber wasted to the cooling jacket of the engine block during the initial heat release portion of the combustion/expansion stroke.
  • the heat that eventually does transfer through the diode coating to the piston body and engine block and head is controlled to keep their temperature lower and assist the functioning of the coating by imposing a lower thermal differential. This also avoids undue thermal expansion of the aluminum piston body.
  • the control can be obtained by: (a) an improved thermally conductive abradable coating on at least the top land of the piston body to conduct available heat to water cooling of the block and the head; (b) spraying oil coolant onto the interior of the piston which oil coolant is preferably isolated from valve train coolant and thus can be at a lower viscosity; and (c) planting of a cast-in-place thermal expansion inhibitor in the piston body adjacent The piston crown.
  • the intake (and exhaust) manifold walls are fabricated to have double walls/air gap insulated construction to prevent the heating of the fresh charge as it travels from the air intake into the engine through the intake ports.
  • the double wall construction features a very thin inner wall (approximately 0.015 to 0.031 inches) a very low thermal conductivity stainless steel. This not only insulates engine heat from flowing into the charge, but also reduces the fuel condensation during a cold start.
  • FIG. 1 is a central sectional elevational view of an internal combustion spark ignition engine depicting the thermal heat management characteristics of this invention
  • FIG. 2 is an enlarged fragmentary sectional view of the coated combustion chamber of FIG. 1;
  • FIG. 3 is a diagram of the physics of heat transfer from a gas mixture through various mediums including a gas skin layer, the coating of this invention, the metal substrate, a liquid skin of coolant, and the liquid coolant itself;
  • FIG. 4 is a schematic representation of how the mediums of FIG. 3 act as resistances to thermal flow
  • FIG. 5 is a greatly enlarged fragmentary cross-sectional view of the upper right hand corner of a piston within a cylinder bore wall of an internal combustion engine embodying more fully the thermal management principles of this invention
  • FIG. 6 is a schematic representation of a single oil path arrangement for lubricating the valve train and combustion area of the engine, the arrangement using dual cooling;
  • FIG. 7 is a schematic representation of a dual oil path arrangement for lubricating different parts of the engine, the arrangement facilitating use of lower viscosity oil in cooling the piston;
  • FIG. 8 is a composite illustration of the stages of a four-stroke cycle engine showing heat flow restriction as a result of the coatings and thereby facilitating higher compression ratios.
  • Heat absorbed by the piston body, particularly the crown surface of a non-coated piston, will transfer the absorbed heat throughout the mass of the piston because of the high thermal conductivity of the piston metal, such as aluminum.
  • the piston will be hotter and weaker.
  • the hotter piston and combustion chamber surfaces adversely affect the temperature of the incoming intake mixture into the combustion chamber during the intake and compression strokes; the intake air/fuel mixture will attain a relatively higher temperature at the end of the intake stroke compared to its start, with a reduced volumetric efficiency.
  • the engine designer will adjust the compression ratio of the spark ignition engine to avoid knock. For example, the combustion gas temperature at the end of the compression stroke must be designed to be lower by limiting the compression ratio.
  • the heat on the skin of the piston crown will auto ignite the combustible mixture in the combustion chamber if it exceeds the designed temperature by 30°-40° F.
  • the piston due to the hotter temperature of the aluminum piston (resulting from the absorbed and diffused heat), the piston will experience a higher thermal expansion characteristic different than the material constituting the cylinder bore wall.
  • the aluminum piston to bore clearance will therefore be increased because of reduced temperature and consequent reduced thermal expansion of the piston. This significantly increases the crevice volume between the piston and bore wall, thereby increasing the high carbon emissions as well as gaseous blow-by pass the piston rings and crown.
  • this invention employs heat management coatings or plys to increase the volumetric efficiency of a heat engine 10, prevent auto ignition at higher compression ratios in the case of a spark ignition engine, and reduce exhaust emissions 11 as well as prevent contamination of the combustion chamber surfaces 12 over the life cycle of the heat engine.
  • a low thermal diffusivity (low alpha) coating 13 operating as a thermal diode, is applied to the piston crown and to the combustion chamber surfaces 15 in the head (see FIG. 2), including valve head surfaces 16.
  • Thermal diffusivity is an expression of the ratio of thermal conductivity watts/meter °K.) to the multiple of density (Kg/meter 3 ) and mass specific heat capacity (Joules/kilogram °K.).
  • a good low thermal diffusivity number for this invention is about half that of that for aluminum, such as 93 ⁇ 10 -6 for Al, zirconia 54 ⁇ 10 -6 , 316 stainless steel 51 ⁇ 10 -6 and Ti alloy 62 ⁇ 10 -6 metric units.
  • the coating must be (i) relatively low in thermal conductivity, (ii) be capable of holding a predetermined desirable quantity of heat calories to limit the conduction of heat in a direction that would be wasted to tooling, and (iii) be sufficiently thin or low enough in mass to limit flow of stored heat in a reverse direction to an incoming colder gas charge.
  • the coating temperature will rise, with little heat transfer going across the coating; then at the end of the exhaust stroke, the piston crown will be cooler, in heating heat flow into the metal components, but not in impeding heat flux out of the components to a coolant.
  • the diode coating will essentially slow down or limit heat transfer to the cooling system, stored heat is limited so as to restrict transfer back to the fresh incoming charge during the intake stroke and compression, and heat that does get into the piston or is readily removed by better conduction paths which will be described subsequently.
  • the diode coating will typically reach a stable temperature of about 375° F. in a spark ignition gasoline engine, allowing the piston crown below the coating to be at least 100° F. cooler, assuming the gas mixture is about 500° F. and the coolant temperature is about 100° F.
  • thermal diffusivity material examples include titanium aluminide, titanium-6Al alloy, zirconium oxide, thorium oxide, and 200 or 300 series stainless steel (u,e, 316 ss) having chromium (of about 20%) and nickel (of about 8%).
  • Thermal conductivity should be low, in the range of near zero to 21 W/M°K.; the density is usually in operable range of 5000-9000 Kg/m 3 ; the specific heat is greater than 500 J/Kg°K.; the thickness of the coating should be in the operable range of 0.75 to 1.22 mm; and the thermal diffusivity is thus about near zero to 62.
  • the thickness 17 of such low diffusivity coating is critical to its functioning as a thermal diode due to cyclic operation (i.e. heating and cooling) of the engine components.
  • the physics of heat loss from the gas mixture 18 can be visualized to thermally consist of a path through a gas boundary layer 19 immediately adjacent the solid metal 20 (or low thermal diffusivity coating 13 in the case of the present invention), through the thickness of the solid metal, and thence through a thin boundary layer 21 of air or water coolant 22 (serving to receive the transfer heat and dump to atmosphere).
  • a thermal gradient through each layer 19, 20 and 21 with the greatest but shortest gradient apparent in layers 19 and 21.
  • the optimum thickness of the coating for the various materials has proven by experimental data to be 0.70 mm for thorium oxide, 0.76 mm for zirconium oxide, 0.80 mm for titanium aluminide, and 0.85 mm for 316 stainless steel
  • the coating is preferably applied by first preparing the crown piston surface 14 and other combustion surfaces 15 and valve head surface 16 to be clean and free of contamination; secondly, the diode coating material is deposited onto such cleaned surface, such as by plasma/thermal spraying onto the piston crown and other combustion chamber surfaces.
  • the thermal diffusivity material can be applied in a powder form injected into the plasma or be dissolution in a solvent for ambient temperature spraying.
  • the plasma sprayed coating should have a bond strength to the piston that exceeds 2000 psi, preferably above 6000 psi, and a porosity of 3-5%.
  • the solvent is filled prior to spraying with appropriate solids such as zirconia, titanium-aluminum alloy or stainless steel, as well as an appropriate bonding agent such as a high temperature polyimide-amide.
  • appropriate solids such as zirconia, titanium-aluminum alloy or stainless steel
  • an appropriate bonding agent such as a high temperature polyimide-amide.
  • the mixture will stick to the substrate, after which the solvent will evaporate.
  • the piston crown 14 has a dished surface 14A, the coating 13 will following the contours of such central dishing (see FIGS. 2 and 5).
  • the particle size of the powder material utilized, in the deposition is within the range of 85-30 microns, but preferably 60-45 microns.
  • the chamber walls may collect isolated or dispersed carbon deposits during operation, which deposits eventually will become coked and create contaminations that induce auto ignition as well as abrasion and scuffing of the cylinder bore when lodged between the piston rings.
  • the thermal diode coating 13 on such surface may also be contaminated by such deposits.
  • an ultra thin overlayer 25 (see FIG. 5) of highly inert material is placed on the thermal diffusivity coating 13.
  • Such deposit prevention coating 25 should be a material that is preferably selected from the group consisting of gold, aluminum bronze, platinum, titanium nitrite, silicon nitrite, nickel aluminide and titanium aluminide.
  • the deposit prevention coating 25 should be applied in a thickness preferably in the range of 100 angstroms to 5 microns. The coating, being very thin, will not interfere with the thermal diode effect of the coating on which it is overlaid.
  • the deposit prevention coating obviously should be stable at extremely high temperatures such as about 1200° F.
  • the thermal diode coating 13 will restrict heat flow to the piston body 27 to the caloric capacity of the coating (thereby lowering the overall temperature of the main body mass of the aluminum piston), the piston body 27 temperature will still be sufficiently high to experience differential thermal expansion with the cylinder bore wall 31 whether the bore wall 31 is a different or the same material.
  • a low thermal expansion/high conductivity insert 26 may be cast-in-place immediately below, but spaced from, the thermal diffusivity layer 13.
  • the insert 26 may have a material selected from the group consisting of solid carbon, (graphite), silicon carbide, silicon nitride, titanium-aluminum alloy or a low expansion ceramic such as cordierite and beta spodumena; other materials can be used as long as they provide compatibility with the aluminum and low thermal expansion and light weight.
  • the insert is fabricated as a metal matrix composite of aluminum powder and low thermal expansion fibers, such as silicon nitride, silicon carbide, or aluminum oxide.
  • the fibers should be desirably aligned in the direction of anticipated thermal growth to inhibit the thermal expansion.
  • the insert may be formed as a perforated pancake, a ring shape, or a sliced disc of a honeycomb matrix.
  • the insert should be cast-in-place by preheating the insert to about 40% of the temperature of molten aluminum to be cast thereabout. The insert will provide the reduced thermal growth from temperature extremes caused by the engine speed/load fluxuations.
  • the top circular land 28 of the piston 29 can have a tenaciously adhered, thermally conductive, abradable coating 30 which promotes a larger conductive thermal path from the piston 29 to the cylinder bore wall 31 of block 32. This allows the piston to (i) remain at a further reduced temperature, and (ii) to achieve substantially zero clearance with the cylinder bore wall 31 regardless of the effectiveness of the piston rings 33.
  • the abradable coating 30 is deposited over the land 28 in a thickness at least equal to, but desirably slightly in excess of any clearance between the land 28 and the cylinder bore wall 31, so that during initial engine operation, the coating 30 will abrade and polish to a smooth surface conforming to the annulus of the cylinder bore wall 31 with essentially little or no radial clearance between the coating and an oil film 34 on the cylinder bore wall 31.
  • abrade in the context of this invention, means that the coating can readily wear under pressure contact against the bore wall.
  • Abradability herein is not meant to include such materials as teflon or polymers that soften and flow to fill the piston ring grooves and thereby adversely impact ring function.
  • the enlarged direct thermal path from the piston through the abradable coating 30 is achieved by incorporation of conductive particles or flakes 35, such as copper or aluminum, in the coating matrix; copper flake is the preferred medium.
  • the piston can operate within the cylinder bore wall with no more than a gas squeeze film lubrication therebetween, assuming the oil film on the cylinder bore wall should fail.
  • the clearance between the coating 30 and the cylinder bore wall 31 or oil film 34 thereon is designed or allowed to become greater than 5 microns (for example, up to 10-15 microns) then the abradable coating should contain a required content of solid film lubricants.
  • Such solid lubricants are defined to comprehend material that have coefficient of friction no greater than 0.06 at 400°-700° F.
  • a coating that meets such criteria preferably comprises a mixture of at least two elements selected from the group consisting of graphite, molybdenum disulfide and boron nitride; the mixture is carried in a polymer emulsion for deposition, the polymer (polyamide or epoxy thermoset type) adhering the film coating to the land surface.
  • the piston interior 29A may be sprayed with oil from the crankcase sump 37.
  • the oil may be drawn and pumped from the sump 37 and carried up the connecting rod 38 and thereafter sprayed through radial openings 39 in the connecting rod small end 38A to bathe the interior surface 29A of the piston 29.
  • Such oil spray cooling of the underside 29A of the piston, and splash cooling of the cylinder wall 34, will maintain the piston-cylinder bore clearance 40 in the designed range, which preferably is essentially 0.
  • the resulting overheating of the piston crown and its enlargement would ordinarily cause engine failure; the abradable coating prevents catastrophic failure.
  • a dual cooling single circuit for a V-8 engine block comprises a main line oil pump 40 which delivers pressurized fluid along a line 41 to an oil filter 42 and a first oil cooler 43 and thence to a main horizontal returning line 44.
  • Downward feeding lines 45, 46, 47 and 48 (from four stations along the main return line 44) supply oil respectively to crankshaft bearings 49.
  • Upward feeding lines 51 and 52 each supply oil respectively to valve train layout 53,54 for each engine head on each side of the V-configuration block; oil returns to sump 55 from layouts 53, 54 by lines not shown.
  • a second cooler 62 is used, in a line 64 to cool oil taken off the line 63 coming out of the first oil cooler 43; line 64 divides and connects to valve train layouts at other locations.
  • the second oil cooler 62 should maintain oil to a maximum temperature of about 160° F. Such reduced temperature facilitates lowering the overall temperature of the engine heads and thereby limits the heat that can transfer to the intake charge from the intake ports and intake manifold.
  • FIG. 7 shows an arrangement where the oil circulated to the valve train layouts is isolated from the main oil circuit 80 for the pistons and cylinder walls; such isolated oil circuit 81 has its own small electric oil pump 82 to provide circulation.
  • Oil cooling for the interior of pistons 56 is illustrated by an upwardly extending line 57 carrying oil upwardly to the piston interior.
  • oil to the interior of the piston may be carried through connecting rod 38 or equivalent to be sprayed along the piston interior, and thence returned to sump 55 along path 58.
  • Similar lines 59,60 and 61 extend upwardly from each crankshaft bearing to feed the other pistons along one side of the engine; complementary lines with complementary pumps would feed the pistons on the other side of the engine.
  • Oil to the eight cylinder bore walls is splashed from ports in the crankshaft bearings, such as designated by 70, 71, 72, 73, 74, 75, 76 and 77.
  • the oil for this circuit 80 should be lower in viscosity, such as 3 to 5 Cp at 40° C. (compared to 100 Cp for conventional engine oil systems) because the lower viscosity reduces engine friction and oil pump power losses at well below 0° F.
  • the importance of isolating the piston-cylinder wall circuit is to facilitate low friction and easy pumping at very cold temperatures.
  • the invention in another aspect, is a method of thermally managing heat generated by an internal combustion engine having to move a piston along a wall, such engine having a combustion chamber for combusting a gaseous mixture of air and fuel, and further having a cooling jacket for cooling such wall.
  • the method comprises increasing the compression ratio of the engine (i.e. about 10-20%); coating the crown of the piston that faces the combustion chamber with a low thermal diffusivity layer that functions as a heat diode; and operating the engine with such coated piston and increased compression ratio whereby a fresh intake mixture to the combustion chamber will be drawn thereinto at a lower temperature in greater volumetric efficiency and with less heat from the piston crown transferred to such charge. Less heat from combustion will be wasted to the cooling jacket.
  • the compression ratio can be increased from about 8:1 to about 10:1.
  • the fresh intake mixture to the engine can be decreased in temperature from about 160° F. to about 120° F. at the start of the compression stroke. Less heat is transferred to the charge by exposure to the coated layer of the piston whereby snored heat from a previous piston operation cycle is prevented from heating this fresh charge prior to combustion.
  • the thickness of the coating should be minimized to satisfy the equation for low diffusivity (i.e. less than 1 mm).
  • stage one the coated piston is almost to the completion of an exhaust stroke with only the exhaust valve open. With a very short travel to the total completion of the exhaust stroke (as in stage two) both intake and exhaust valves will be opened.
  • stage three As the inducted charge is drawn into the cylinder bore (stage three) at about a temperature of 90°-100° F. (typical of intake duct temperatures), a transfer of heat takes place from the coating 13 (previously heated by cyclic operation) but is severely limited by the caloric content of the coating and by the restricted thermal conductivity of the coating. Such charge will rise in temperature to about 120° F. during induction. Since a greater mass of mixture can now be introduced to the combustion chamber due to its lower temperature of 120° F.
  • the volumetric efficiency is increased, allowing the engine designer to increase the compression ratio (for example from about 8:1 to 10:1) without fear of the charge reaching the auto ignition temperature (i.e. of about 800° F.) during the compression stroke (stage four).
  • the coating restricts heat transfer to the charge from the combustion chamber walls during compression by the nature of its low diffusivity. Ignition takes place (stage five) and during expansion, throttle heat transferred to the piston and chamber walls will occur as a result of the presence of the low diffusivity coating, which reserves a greater amount of combustion heat to do work during such power stroke.
  • the thermal diode coating may further be protected with a deposit preventing coating, such as gold in a whisper thin layer.
  • the method may further comprehend fabricating the piston to not only have a heat diode coating on its crown, but also a low thermal expansion high conductivity implant immediately below the diode coating. This retains the shape of the crown to accommodate the thermal expansion changes resulting from engine speed/load fluxuations and to rapidly dissipate heat into the oil spray to minimize the temperature rise in the piston.
  • the method may further comprehend fabricating the piston to provide for increased heat sink capabilities such as (i) a thermally conductive abradable top land coating, effective to transfer heat to the engine block, and/or (ii) an oil spray system for bathing the interior surfaces of the piston with oil effective to transfer heat to the oil cooling system of the engine.
  • a thermally conductive abradable top land coating effective to transfer heat to the engine block
  • an oil spray system for bathing the interior surfaces of the piston with oil effective to transfer heat to the oil cooling system of the engine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
US08/315,162 1994-09-29 1994-09-29 Thermal management system for heat engine components Expired - Lifetime US5477820A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US08/315,162 US5477820A (en) 1994-09-29 1994-09-29 Thermal management system for heat engine components
DE19524015A DE19524015C2 (de) 1994-09-29 1995-06-30 Verbrennungsmotor mit mindestens einer Kolben/Brennkammeranordnung
JP7192066A JPH08100659A (ja) 1994-09-29 1995-07-27 熱エンジンのピストン及び燃焼チェンバーの構造及びエンジンの熱の熱的管理方法
GB9516811A GB2293863B (en) 1994-09-29 1995-08-16 Thermal management system for engine components
CA002159232A CA2159232A1 (en) 1994-09-29 1995-09-27 Thermal management system for heat engine components

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US08/315,162 US5477820A (en) 1994-09-29 1994-09-29 Thermal management system for heat engine components

Publications (1)

Publication Number Publication Date
US5477820A true US5477820A (en) 1995-12-26

Family

ID=23223177

Family Applications (1)

Application Number Title Priority Date Filing Date
US08/315,162 Expired - Lifetime US5477820A (en) 1994-09-29 1994-09-29 Thermal management system for heat engine components

Country Status (5)

Country Link
US (1) US5477820A (de)
JP (1) JPH08100659A (de)
CA (1) CA2159232A1 (de)
DE (1) DE19524015C2 (de)
GB (1) GB2293863B (de)

Cited By (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997007328A1 (en) * 1995-08-16 1997-02-27 Northrop-Grumman Corporation Fiber reinforced ceramic matrix composite cylinder head and cylinder head liner for an internal combustion engine
US5657729A (en) * 1995-08-16 1997-08-19 Northrop Grumman Corporation Fiber reinforced ceramic matrix composite cylinder head and cylinder head liner for an internal combustion engine
US5887558A (en) * 1994-10-15 1999-03-30 Motorenfabrik Hatz Gmbh & Co. Kg Combustion engine
US6022594A (en) * 1996-12-23 2000-02-08 General Electric Company Method to improve the service life of zirconia-based coatings applied by plasma spray techniques, using uniform coating particle size
US6170441B1 (en) 1998-06-26 2001-01-09 Quantum Energy Technologies Engine system employing an unsymmetrical cycle
US6250263B1 (en) 1999-04-28 2001-06-26 Mark Sisco Dual piston cylinder configuration for internal combustion engine
WO2003067052A1 (de) * 2002-02-06 2003-08-14 Man B & W Diesel A/S Motor
US6688867B2 (en) * 2001-10-04 2004-02-10 Eaton Corporation Rotary blower with an abradable coating
US20050274333A1 (en) * 2004-02-09 2005-12-15 Benmaxx, Llc Fluid-cooled cylinder liner
US20060000351A1 (en) * 2004-06-30 2006-01-05 Schenkel Jerry L Piston for an engine
US7066132B1 (en) * 2005-01-13 2006-06-27 General Motors Corporation Piston with oxidation catalyst
US20070084449A1 (en) * 2005-10-18 2007-04-19 Najt Paul M Method to improve combustion stability in a controlled auto-ignition combustion engine
US20080250923A1 (en) * 2007-03-29 2008-10-16 Toyoda Gosei Co., Ltd. Piston and process for manufacturing the same
US7527048B2 (en) * 2001-08-01 2009-05-05 Diesel Engine Transformation Llc Catalytic combustion surfaces and method for creating catalytic combustion surfaces
US20110144882A1 (en) * 2010-08-31 2011-06-16 Ford Global Technologies, Llc Approach for variable pressure oil injection
US20110271916A1 (en) * 2010-05-04 2011-11-10 Ford Global Technologies, Llc Internal Combustion Engine with Liquid Cooling
US20130133609A1 (en) * 2011-11-28 2013-05-30 Eduardo Matsuo Piston with anti-carbon deposit coating and method of construction thereof
US20130239924A1 (en) * 2010-12-02 2013-09-19 Toyota Jidosha Kabushiki Kaisha Heat-shielding film and method of forming the same
US20140345559A1 (en) * 2013-05-27 2014-11-27 Aisin Seiki Kabushiki Kaisha Mechanical component for internal combustion engine, manufacturing method of mechanical component for internal combustion engine, and mechanical component
WO2015034448A1 (en) * 2013-09-03 2015-03-12 Ford Otomotiv Sanayi Anonim Sirketi A combustion system with a heat recovery unit
US20150226150A1 (en) * 2012-09-11 2015-08-13 Mahle Metal Leve S/A Engine piston and a process for making an engine piston
EP3070312A1 (de) * 2015-03-17 2016-09-21 Toyota Jidosha Kabushiki Kaisha Kolben für einen verbrennungsmotor, verbrennungsmotor mit diesem kolben und herstellungsverfahren dieses kolbens
US20170159584A1 (en) * 2015-12-08 2017-06-08 Toyota Jidosha Kabushiki Kaisha Control device for internal combustion engine
US9683480B2 (en) 2012-03-30 2017-06-20 Kabushiki Kaisha Toyota Chuo Kenkyusho Spark ignition type internal combustion engine
RU2624091C1 (ru) * 2015-03-17 2017-06-30 Тойота Дзидося Кабусики Кайся Поршень для двигателя внутреннего сгорания, двигатель внутреннего сгорания с таким поршнем и способ изготовления такого поршня
US20170284281A1 (en) * 2014-10-07 2017-10-05 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
CN107269412A (zh) * 2016-04-08 2017-10-20 丰田自动车株式会社 内燃机
US9810174B2 (en) 2011-11-04 2017-11-07 Achates Power, Inc. Constructions for piston thermal management
US9909528B2 (en) 2014-02-04 2018-03-06 Federal-Mogul Llc Piston with abradable coating to generate appropriate contact geometry on running surface
US20180106212A1 (en) * 2016-10-19 2018-04-19 Toyota Jidosha Kabushiki Kaisha Manufacturing method for engine
US10508615B2 (en) 2017-10-30 2019-12-17 Ford Global Technologies, Llc Engine with a piston heating system and method for operation thereof
US10519854B2 (en) 2015-11-20 2019-12-31 Tenneco Inc. Thermally insulated engine components and method of making using a ceramic coating
US10578050B2 (en) 2015-11-20 2020-03-03 Tenneco Inc. Thermally insulated steel piston crown and method of making using a ceramic coating
US11155721B2 (en) 2017-07-06 2021-10-26 General Electric Company Articles for high temperature service and related method
WO2024044506A1 (en) * 2022-08-22 2024-02-29 Cummins Inc. Multi-composition thermal management coating systems for combustion chamber components

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19857071A1 (de) * 1998-12-10 2000-06-15 Volkswagen Ag Verbrennungsmotor
DE10322304A1 (de) * 2003-05-17 2004-12-02 Daimlerchrysler Ag Ölversorgungssystem für eine Brennkraftmaschine
JP4748078B2 (ja) * 2007-02-16 2011-08-17 株式会社豊田中央研究所 内燃機関
JP2013227910A (ja) * 2012-04-25 2013-11-07 Isuzu Motors Ltd エンジンの燃焼室構造
DE102015201847A1 (de) 2015-02-03 2016-08-04 Volkswagen Aktiengesellschaft Verbrennungskraftmaschine für ein Kraftfahrzeug
AT517589B1 (de) 2015-07-03 2017-03-15 Ge Jenbacher Gmbh & Co Og Kolben für eine Brennkraftmaschine

Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2410405A (en) * 1945-01-01 1946-11-05 Richard T Cornelius Piston
US2519683A (en) * 1947-09-17 1950-08-22 Ramsey Corp Piston ring
US2575214A (en) * 1948-09-30 1951-11-13 Wright Aeronautical Corp Piston with plated piston ring grooves
US2609260A (en) * 1950-02-23 1952-09-02 Ramsey Corp Piston packing ring
US3012831A (en) * 1957-05-03 1961-12-12 Gould National Batteries Inc Piston for internal combustion engines
US3095204A (en) * 1961-03-08 1963-06-25 California Research Corp Wear-resistant lining for piston-ring groove
US3890950A (en) * 1973-10-02 1975-06-24 Megatech Corp Piston lubricating
US3917290A (en) * 1972-11-28 1975-11-04 Robert Geffroy Assembly comprising a piston groove, a piston ring and an inertia ring sliding in a cylinder
US3938814A (en) * 1974-09-23 1976-02-17 Koppers Company, Inc. Bearing member having a wear resistant coating on its bearing face
US3942808A (en) * 1973-05-25 1976-03-09 Midland-Ross Corporation Piston ring assembly
US3974309A (en) * 1973-12-26 1976-08-10 Ford Motor Company Method of coating a rotary internal combustion engine
US4495907A (en) * 1983-01-18 1985-01-29 Cummins Engine Company, Inc. Combustion chamber components for internal combustion engines
US4599270A (en) * 1984-05-02 1986-07-08 The Perkin-Elmer Corporation Zirconium oxide powder containing cerium oxide and yttrium oxide
US4612260A (en) * 1984-08-09 1986-09-16 Nippon Piston Ring Co., Ltd. Piston ring member
US4852542A (en) * 1987-10-23 1989-08-01 Adiabatics, Inc. Thin thermal barrier coating for engines
US4867119A (en) * 1988-10-21 1989-09-19 Caterpillar Inc. Engine piston assembly and forged piston member therefor having a cooling recess
US5038725A (en) * 1988-12-02 1991-08-13 Hitachi, Ltd. Intake manifold of internal combustion engine
US5133564A (en) * 1989-06-30 1992-07-28 Goldstar Co., Ltd. Piston ring assembly for stirling engine
US5236787A (en) * 1991-07-29 1993-08-17 Caterpillar Inc. Thermal barrier coating for metallic components
US5305726A (en) * 1992-09-30 1994-04-26 United Technologies Corporation Ceramic composite coating material

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2817562A (en) * 1953-07-01 1957-12-24 Gen Motors Corp Coated piston
US3855986A (en) * 1972-03-15 1974-12-24 J Wiss Reflectively coated combustion chamber for internal combustion engines and method of using same
GB1519966A (en) * 1974-07-15 1978-08-02 Townsend Engineering Co Internal combustion engine and method for cooling the sam
CA1200166A (en) * 1980-08-22 1986-02-04 Jay D. Rynbrandt Internal combustion engine having manifold and combustion surfaces coated with a foam
BR8500556A (pt) * 1985-02-07 1986-09-09 Metal Leve S/A. Industria E Comercio Processo de fabricacao de embolo e embolo para motores de combustao interna
JP2718071B2 (ja) * 1988-07-21 1998-02-25 いすゞ自動車株式会社 副室式断熱エンジン
DE9010077U1 (de) * 1989-08-07 1990-10-04 Alcan Deutschland GmbH, 3400 Göttingen Verbrennungskraftmaschine
JPH04106556U (ja) * 1991-02-28 1992-09-14 株式会社アツギユニシア アルミニウム合金製ピストン
WO1993024672A1 (en) * 1992-05-29 1993-12-09 United Technologies Corporation Ceramic thermal barrier coating for rapid thermal cycling applications
US5239955A (en) * 1993-01-07 1993-08-31 Ford Motor Company Low friction reciprocating piston assembly

Patent Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2410405A (en) * 1945-01-01 1946-11-05 Richard T Cornelius Piston
US2519683A (en) * 1947-09-17 1950-08-22 Ramsey Corp Piston ring
US2575214A (en) * 1948-09-30 1951-11-13 Wright Aeronautical Corp Piston with plated piston ring grooves
US2609260A (en) * 1950-02-23 1952-09-02 Ramsey Corp Piston packing ring
US3012831A (en) * 1957-05-03 1961-12-12 Gould National Batteries Inc Piston for internal combustion engines
US3095204A (en) * 1961-03-08 1963-06-25 California Research Corp Wear-resistant lining for piston-ring groove
US3917290A (en) * 1972-11-28 1975-11-04 Robert Geffroy Assembly comprising a piston groove, a piston ring and an inertia ring sliding in a cylinder
US3942808A (en) * 1973-05-25 1976-03-09 Midland-Ross Corporation Piston ring assembly
US3890950A (en) * 1973-10-02 1975-06-24 Megatech Corp Piston lubricating
US3974309A (en) * 1973-12-26 1976-08-10 Ford Motor Company Method of coating a rotary internal combustion engine
US3938814A (en) * 1974-09-23 1976-02-17 Koppers Company, Inc. Bearing member having a wear resistant coating on its bearing face
US4495907A (en) * 1983-01-18 1985-01-29 Cummins Engine Company, Inc. Combustion chamber components for internal combustion engines
US4599270A (en) * 1984-05-02 1986-07-08 The Perkin-Elmer Corporation Zirconium oxide powder containing cerium oxide and yttrium oxide
US4612260A (en) * 1984-08-09 1986-09-16 Nippon Piston Ring Co., Ltd. Piston ring member
US4852542A (en) * 1987-10-23 1989-08-01 Adiabatics, Inc. Thin thermal barrier coating for engines
US4867119A (en) * 1988-10-21 1989-09-19 Caterpillar Inc. Engine piston assembly and forged piston member therefor having a cooling recess
US5038725A (en) * 1988-12-02 1991-08-13 Hitachi, Ltd. Intake manifold of internal combustion engine
US5133564A (en) * 1989-06-30 1992-07-28 Goldstar Co., Ltd. Piston ring assembly for stirling engine
US5236787A (en) * 1991-07-29 1993-08-17 Caterpillar Inc. Thermal barrier coating for metallic components
US5305726A (en) * 1992-09-30 1994-04-26 United Technologies Corporation Ceramic composite coating material

Cited By (52)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5887558A (en) * 1994-10-15 1999-03-30 Motorenfabrik Hatz Gmbh & Co. Kg Combustion engine
US5657729A (en) * 1995-08-16 1997-08-19 Northrop Grumman Corporation Fiber reinforced ceramic matrix composite cylinder head and cylinder head liner for an internal combustion engine
WO1997007328A1 (en) * 1995-08-16 1997-02-27 Northrop-Grumman Corporation Fiber reinforced ceramic matrix composite cylinder head and cylinder head liner for an internal combustion engine
US6022594A (en) * 1996-12-23 2000-02-08 General Electric Company Method to improve the service life of zirconia-based coatings applied by plasma spray techniques, using uniform coating particle size
US6170441B1 (en) 1998-06-26 2001-01-09 Quantum Energy Technologies Engine system employing an unsymmetrical cycle
AU745701B2 (en) * 1998-06-26 2002-03-28 Supercritical Combustion Corporation Engine system employing an unsymmetrical cycle
AU745701C (en) * 1998-06-26 2003-04-17 Supercritical Combustion Corporation Engine system employing an unsymmetrical cycle
US6250263B1 (en) 1999-04-28 2001-06-26 Mark Sisco Dual piston cylinder configuration for internal combustion engine
US7527048B2 (en) * 2001-08-01 2009-05-05 Diesel Engine Transformation Llc Catalytic combustion surfaces and method for creating catalytic combustion surfaces
US6688867B2 (en) * 2001-10-04 2004-02-10 Eaton Corporation Rotary blower with an abradable coating
WO2003067052A1 (de) * 2002-02-06 2003-08-14 Man B & W Diesel A/S Motor
US7290506B2 (en) * 2004-02-09 2007-11-06 Benmaxx, Llc Fluid-cooled cylinder liner
US20050274333A1 (en) * 2004-02-09 2005-12-15 Benmaxx, Llc Fluid-cooled cylinder liner
US20060000351A1 (en) * 2004-06-30 2006-01-05 Schenkel Jerry L Piston for an engine
US7051645B2 (en) 2004-06-30 2006-05-30 Briggs & Stratton Corporation Piston for an engine
US7066132B1 (en) * 2005-01-13 2006-06-27 General Motors Corporation Piston with oxidation catalyst
US20060150941A1 (en) * 2005-01-13 2006-07-13 Verbrugge Mark W Piston with oxidation catalyst
US20070084449A1 (en) * 2005-10-18 2007-04-19 Najt Paul M Method to improve combustion stability in a controlled auto-ignition combustion engine
US7802553B2 (en) * 2005-10-18 2010-09-28 Gm Global Technology Operations, Inc. Method to improve combustion stability in a controlled auto-ignition combustion engine
US20080250923A1 (en) * 2007-03-29 2008-10-16 Toyoda Gosei Co., Ltd. Piston and process for manufacturing the same
US8601987B2 (en) * 2010-05-04 2013-12-10 Ford Global Technologies, Llc Internal combustion engine with liquid cooling
US20110271916A1 (en) * 2010-05-04 2011-11-10 Ford Global Technologies, Llc Internal Combustion Engine with Liquid Cooling
US9453439B2 (en) 2010-08-31 2016-09-27 Ford Global Technologies, Llc Approach for variable pressure oil injection
US20110144882A1 (en) * 2010-08-31 2011-06-16 Ford Global Technologies, Llc Approach for variable pressure oil injection
US9051876B2 (en) * 2010-12-02 2015-06-09 Toyota Jidosha Kabushiki Kaisha Heat-shielding film and method of forming the same
US20130239924A1 (en) * 2010-12-02 2013-09-19 Toyota Jidosha Kabushiki Kaisha Heat-shielding film and method of forming the same
US9810174B2 (en) 2011-11-04 2017-11-07 Achates Power, Inc. Constructions for piston thermal management
US20130133609A1 (en) * 2011-11-28 2013-05-30 Eduardo Matsuo Piston with anti-carbon deposit coating and method of construction thereof
US9169800B2 (en) * 2011-11-28 2015-10-27 Federal-Mogul Corporation Piston with anti-carbon deposit coating and method of construction thereof
US9683480B2 (en) 2012-03-30 2017-06-20 Kabushiki Kaisha Toyota Chuo Kenkyusho Spark ignition type internal combustion engine
US20150226150A1 (en) * 2012-09-11 2015-08-13 Mahle Metal Leve S/A Engine piston and a process for making an engine piston
US9611803B2 (en) * 2012-09-11 2017-04-04 Mahle Metal Leve S/A Engine piston and a process for making an engine piston
US20140345559A1 (en) * 2013-05-27 2014-11-27 Aisin Seiki Kabushiki Kaisha Mechanical component for internal combustion engine, manufacturing method of mechanical component for internal combustion engine, and mechanical component
US10094025B2 (en) * 2013-05-27 2018-10-09 Aisin Seiki Kabushiki Kaisha Mechanical component for internal combustion engine, manufacturing method of mechanical component for internal combustion engine, and mechanical component
US20170268109A1 (en) * 2013-05-27 2017-09-21 Aisin Seiki Kabushiki Kaisha Mechanical component for internal combustion engine, manufacturing method of mechanical component for internal combustion engine, and mechanical component
WO2015034448A1 (en) * 2013-09-03 2015-03-12 Ford Otomotiv Sanayi Anonim Sirketi A combustion system with a heat recovery unit
US9909528B2 (en) 2014-02-04 2018-03-06 Federal-Mogul Llc Piston with abradable coating to generate appropriate contact geometry on running surface
US20170284281A1 (en) * 2014-10-07 2017-10-05 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
US10309293B2 (en) * 2014-10-07 2019-06-04 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
RU2624091C1 (ru) * 2015-03-17 2017-06-30 Тойота Дзидося Кабусики Кайся Поршень для двигателя внутреннего сгорания, двигатель внутреннего сгорания с таким поршнем и способ изготовления такого поршня
EP3070312A1 (de) * 2015-03-17 2016-09-21 Toyota Jidosha Kabushiki Kaisha Kolben für einen verbrennungsmotor, verbrennungsmotor mit diesem kolben und herstellungsverfahren dieses kolbens
US10519854B2 (en) 2015-11-20 2019-12-31 Tenneco Inc. Thermally insulated engine components and method of making using a ceramic coating
US10578050B2 (en) 2015-11-20 2020-03-03 Tenneco Inc. Thermally insulated steel piston crown and method of making using a ceramic coating
US20170159584A1 (en) * 2015-12-08 2017-06-08 Toyota Jidosha Kabushiki Kaisha Control device for internal combustion engine
US10436129B2 (en) * 2015-12-08 2019-10-08 Toyota Jidosha Kabushiki Kaisha Control device for internal combustion engine
CN107269412A (zh) * 2016-04-08 2017-10-20 丰田自动车株式会社 内燃机
US20180106212A1 (en) * 2016-10-19 2018-04-19 Toyota Jidosha Kabushiki Kaisha Manufacturing method for engine
US10539093B2 (en) * 2016-10-19 2020-01-21 Toyota Jidosha Kabushiki Kaisha Manufacturing method for engine
US11155721B2 (en) 2017-07-06 2021-10-26 General Electric Company Articles for high temperature service and related method
US11851581B2 (en) 2017-07-06 2023-12-26 General Electric Company Articles for high temperature service and related method
US10508615B2 (en) 2017-10-30 2019-12-17 Ford Global Technologies, Llc Engine with a piston heating system and method for operation thereof
WO2024044506A1 (en) * 2022-08-22 2024-02-29 Cummins Inc. Multi-composition thermal management coating systems for combustion chamber components

Also Published As

Publication number Publication date
DE19524015C2 (de) 2001-02-22
CA2159232A1 (en) 1996-03-30
DE19524015A1 (de) 1996-04-04
GB2293863A (en) 1996-04-10
GB9516811D0 (en) 1995-10-18
GB2293863B (en) 1998-05-13
JPH08100659A (ja) 1996-04-16

Similar Documents

Publication Publication Date Title
US5477820A (en) Thermal management system for heat engine components
US5469777A (en) Piston assembly having abradable coating
US10001038B2 (en) Heat-insulated system for lubricating rotating and oscillating components of a motor vehicle
US4711208A (en) Piston for internal combustion engines
US4872432A (en) Oilless internal combustion engine having gas phase lubrication
JPH0350331A (ja) アルコール燃料を用いるセラミックエンジン
US5029562A (en) Hybrid piston for high temperature engine
Robinson et al. A review of precision engine cooling
US6349681B1 (en) Cylinder block for internal combustion engine
US6321699B1 (en) Spheroidal rotary valve for combustion engines
Crabb et al. New modular engine platform from Volvo
USRE34143E (en) Oilless internal combustion engine having gas phase lubrication
GB2156038A (en) Piston for internal combustion engine
CA2028713C (en) Polymetallic piston-cylinder configuration for internal combustion engines
GB2442736A (en) Cooling internal combustion engines
Funatani et al. Composite coatings improve engines
Usui et al. Effect of diamond-like carbon coating on anti-scuffing characteristics of piston pins
JP2001159369A (ja) エンジンの冷却構造
US20180313294A1 (en) Thermal barrier coating for engine combustion component
Li Thermal and mechanical behavior of an L-4 engine
Hay et al. Design study for a low heat loss version of the Dover engine
JP3063104B2 (ja) アルコールエンジンの潤滑装置
Timoney No Coolant Diesel Engine
JP2623621B2 (ja) エンジンの構造
Khoshravan Heat Transfer Studies in an Adiabatic Diesel Engine

Legal Events

Date Code Title Description
AS Assignment

Owner name: FORD MOTOR COMPANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:RAO, V. DURGA NAGESWAR;REEL/FRAME:007412/0975

Effective date: 19940928

STCF Information on status: patent grant

Free format text: PATENTED CASE

FPAY Fee payment

Year of fee payment: 4

AS Assignment

Owner name: MID-AMERICA COMMERCIALIZATION CORPORATION, A CORP.

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:FORD MOTOR COMPANY;REEL/FRAME:011369/0412

Effective date: 20001031

AS Assignment

Owner name: FORD GLOBAL TECHNOLOGIES, INC. A MICHIGAN CORPORAT

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:FORD MOTOR COMPANY, A DELAWARE CORPORATION;REEL/FRAME:011467/0001

Effective date: 19970301

AS Assignment

Owner name: MID-AMERICA COMMERCIALIZATION, KANSAS

Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE ASSIGNOR, PREVIOUSLY RECORDED AT REEL 011369 FRAME 0412;ASSIGNOR:FORD GLOBAL TECHNOLOGIES, INC.;REEL/FRAME:011783/0528

Effective date: 20001201

FEPP Fee payment procedure

Free format text: PAYER NUMBER DE-ASSIGNED (ORIGINAL EVENT CODE: RMPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 8

AS Assignment

Owner name: FORD GLOBAL TECHNOLOGIES, LLC, MICHIGAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:NATIONAL INSTITUTE FOR STRATEGIC TECHNOLOGY ACQUISITION AND COMMERCIALIZATION;REEL/FRAME:017468/0050

Effective date: 20060405

FEPP Fee payment procedure

Free format text: PAT HOLDER NO LONGER CLAIMS SMALL ENTITY STATUS, ENTITY STATUS SET TO UNDISCOUNTED (ORIGINAL EVENT CODE: STOL); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 12

AS Assignment

Owner name: NATIONAL INSTITUTE FOR STRATEGIC TECHNOLOGY ACQUIS

Free format text: CHANGE OF NAME;ASSIGNOR:MID-AMERICA COMMERCIALIZATION CORPORATION;REEL/FRAME:019955/0279

Effective date: 20040628

SULP Surcharge for late payment
AS Assignment

Owner name: KSU INSTITUTE FOR COMMERCIALIZATION, KANSAS

Free format text: CHANGE OF NAME;ASSIGNORS:MID-AMERICA COMMERCIALIZATION CORPORATION;NATIONAL INSTITUTE FOR STRATEGIC TECHNOLOGY ACQUISITION AND COMMERCIALIZATION;REEL/FRAME:027472/0361

Effective date: 20111011

AS Assignment

Owner name: KANSAS STATE UNIVERSITY INSTITUTE FOR COMMERCIALIZ

Free format text: CHANGE OF NAME;ASSIGNOR:KSU INSTITUTE FOR COMMERCIALIZATION;REEL/FRAME:027544/0951

Effective date: 20111011